EP0150014A2 - Heat pump - Google Patents

Heat pump Download PDF

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Publication number
EP0150014A2
EP0150014A2 EP85100154A EP85100154A EP0150014A2 EP 0150014 A2 EP0150014 A2 EP 0150014A2 EP 85100154 A EP85100154 A EP 85100154A EP 85100154 A EP85100154 A EP 85100154A EP 0150014 A2 EP0150014 A2 EP 0150014A2
Authority
EP
European Patent Office
Prior art keywords
heat pump
water
evaporator
condenser
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP85100154A
Other languages
German (de)
French (fr)
Other versions
EP0150014A3 (en
EP0150014B1 (en
Inventor
Sanji Tokuno
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KH Neochem Co Ltd
Original Assignee
Kyowa Hakko Kogyo Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kyowa Hakko Kogyo Co Ltd filed Critical Kyowa Hakko Kogyo Co Ltd
Publication of EP0150014A2 publication Critical patent/EP0150014A2/en
Publication of EP0150014A3 publication Critical patent/EP0150014A3/en
Application granted granted Critical
Publication of EP0150014B1 publication Critical patent/EP0150014B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
    • F22B3/04—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by drop in pressure of high-pressure hot water within pressure- reducing chambers, e.g. in accumulators
    • F22B3/045—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by drop in pressure of high-pressure hot water within pressure- reducing chambers, e.g. in accumulators the drop in pressure being achieved by compressors, e.g. with steam jet pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D3/00—Distillation or related exchange processes in which liquids are contacted with gaseous media, e.g. stripping
    • B01D3/007—Energy recuperation; Heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency

Definitions

  • This invention relates to an improved mechanical compression type heat pump.
  • a so-called Freon-type refrigerant is generally used in the conventional mechanical compression type heat pump.
  • Freon-type refrigerant is used for a long period under medium or high temperatures, the refrigerant is decomposed into HC1,'HF, etc. If water is introduced into the pump, the pump will be damaged by corrosion.
  • a refrigerant leak brings problems of toxicity, danger, and corrosion for some kinds of refrigerant. Jobs such as regular and irregular supplying of a refrigerant, collection of a refrigerant at the time of repair and overhaul, and refilling of a refrigerant are troublesome. Also, the price of a refrigerant itself is expensive.
  • the uncondensed gas is exhausted from the condenser by continuous or intermittent suction using a vacuum generating apparatus such as an ejector or vacuum pump and a vacuum is maintained as a result.
  • a vacuum generating apparatus such as an ejector or vacuum pump
  • Water or steam, which exert no effect if they enter, is used as sealing liquid or sealing gas at the seal portion (gland seal, mechanical seal, labyrinth seal, etc.) of the compressor in order to limit entering air as far as possible.
  • the quantity of water as a refrigerant in the system is reduced by purges or exhaustion with a vacuum generating apparatus.
  • a vacuum generating apparatus As a preventive measure, to keep the water levels in the evaporator and condenser constant, water is supplied automatically or manually by a pressurized or unpressurized feedwater device.
  • the water level in the system is increased when the quantity of water or steam entering the system exceeds the quantity discharged from the system.
  • an overflow pipe, double valves, or a suction device is used to drain excessive water and keep the water level in the evaporator and condenser constant.
  • the drain level should be higher than the level at which the feedwater device starts operation.
  • the load regulation of the heat pump is done by the adjustment of the compressor's bypass valve, adjustment of the inlet valve opening angle, or control of the number of revolutions.
  • the heat pump according to the present invention comprises a vacuum generating apparatus, a feedwater device, and a draining device, in addition to an evaporator, a compressor, a condenser and a pressure reducing valve which are conventional elements of a heat pump.
  • the vacuum generating apparatus exhausts uncondensed gas which leaks into the heat pump system, the feedwater device supplies water to compensate for decreased amounts of water in the heat pump, and the draining device drains excessive water from the heat pump system.
  • Figure 1 shows the heat pump, operated at a low or medium temperature; e.g., 10 to 95°C, in which both evaporation and condensation of water is performed under a pressure less than atmospheric pressure: e.g. 1.24 x 10 3 to 84.8 x 10 3 Pa (0.18 to 12.3 p si).
  • Heat source fluid e.q., methanol vapor
  • Fluid to be heated e.g., ethanol
  • inlet 13 is heated with steam which is condensed in the condenser 9, and exits via conduit 14.
  • Water flowing in the heat pump evaporates while cooling or condensing.
  • the heat source fluid in the evaporator and flows into compressor 6 after mist is removed by demister 4. Steam pressurized by compressor 6, temperature of which is raised, passes through pipe 15 and enters condenser 9.
  • the vacuum regulation valve 7, provided half way long pipe 17, keeps condensing pressure to the required value; e.g. 1.59 x 10 3 to 97.9 x 10 Pa, (0.23 to 14.2 psi). Steam is discharged from the system along with uncondensed gas, so supplementation of water becomes necessary. This supplementation of water is effected by feedwater device 3 through pipe 18.
  • Pipe 19 is a steam line for sealing of a seal portion of the compressor (labyrinth type). This steam flows into condenser 9 through pipe 18 along with compressed steam and further flows into evaporator 1 through pipe 16 in the form of condensed water. In the case where the quantity of steam entering into the system exceeds the quantity which is discharged by vacuum generating equipment 8, the level of water in the evaporator goes up. In this case, extra water is drained through pipe 20 by draining device 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Central Heating Systems (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

A heat pump using water as a refrigerant comprises an evaporator (1) equipped with a feedwater control device (3) and a draining device (2), a compressor (6) and a condenser (9) equipped with a vacuum generating means (8).

Description

  • This invention relates to an improved mechanical compression type heat pump.
  • A so-called Freon-type refrigerant is generally used in the conventional mechanical compression type heat pump. However, when Freon-type refrigerant is used for a long period under medium or high temperatures, the refrigerant is decomposed into HC1,'HF, etc. If water is introduced into the pump, the pump will be damaged by corrosion. Furthermore, since the whole system is operated under high pressure, a refrigerant leak brings problems of toxicity, danger, and corrosion for some kinds of refrigerant. Jobs such as regular and irregular supplying of a refrigerant, collection of a refrigerant at the time of repair and overhaul, and refilling of a refrigerant are troublesome. Also, the price of a refrigerant itself is expensive.
  • An improved type heat pump, which uses water as a refrigerant, was produced as a result of various studies of improving the above disadvantages. It was found that the heat pump can be operated under pressures below atmospheric pressure.
  • When water is used as a refrigerant, the following three combinations of pressure at the suction and discharge sides of the compressor exist depending on the temperature conditions:
    • 1. The pressure at both suction and discharge sides of the compressor is above atmospheric pressure.
    • 2. The pressure at the suction side is below atmospheric pressure, while the pressure at the discharge side is above atmospheric pressure.
    • 3. The pressure at both suction and discharge sides is below atmospheric pressure.
  • It is impossible to prevent air from entering into the heat pump system when the pressure is below atmospheric pressure at the suction side or at both suction and discharge sides.
  • In the case where the pressure is below atmospheric pressure at only the suction side, while the pressure is above atmospheric pressure at the discharge side, an uncondensed gas (air) is purged from the upper portion of the condenser.
  • In the case where the pressure at both suction and discharge sides is below atmospheric pressure, the uncondensed gas is exhausted from the condenser by continuous or intermittent suction using a vacuum generating apparatus such as an ejector or vacuum pump and a vacuum is maintained as a result.
  • Water or steam, which exert no effect if they enter, is used as sealing liquid or sealing gas at the seal portion (gland seal, mechanical seal, labyrinth seal, etc.) of the compressor in order to limit entering air as far as possible.
  • The quantity of water as a refrigerant in the system is reduced by purges or exhaustion with a vacuum generating apparatus. As a preventive measure, to keep the water levels in the evaporator and condenser constant, water is supplied automatically or manually by a pressurized or unpressurized feedwater device.
  • On the contracy, the water level in the system is increased when the quantity of water or steam entering the system exceeds the quantity discharged from the system.
  • To prevent this, an overflow pipe, double valves, or a suction device is used to drain excessive water and keep the water level in the evaporator and condenser constant.
  • In this case, when draining is done automatically, the drain level should be higher than the level at which the feedwater device starts operation.
  • The load regulation of the heat pump is done by the adjustment of the compressor's bypass valve, adjustment of the inlet valve opening angle, or control of the number of revolutions.
  • The heat pump according to the present invention comprises a vacuum generating apparatus, a feedwater device, and a draining device, in addition to an evaporator, a compressor, a condenser and a pressure reducing valve which are conventional elements of a heat pump.
  • The vacuum generating apparatus exhausts uncondensed gas which leaks into the heat pump system, the feedwater device supplies water to compensate for decreased amounts of water in the heat pump, and the draining device drains excessive water from the heat pump system.
  • The present invention has the following advantages:
    • (1) There is no fear of decomposition of refrigerant and change in quality, because water is used as a refrigerant, and this fact enables the heat pump to be operated over a wide temperature range.
    • (2) In the case of a leak, there is no problem with regard to toxicity, danger or corrosion.
    • (3) Feeding and draining of refrigerant are easy.
    • (4) The refrigerant is inexpensive.
    • (5) As the portions which contact the refrigerant or gas, inexpensive materials such as cast iron and structural steel are used.
    • (6) Since the refrigerant is water, water and steam can be used for sealing at the seal portion of compressor which enhances the degree of seal tightness of the system.
    • (7) Operation and maintenance are easy.
    • (8) In the case where operation is carried out under pressures below atmospheric pressure, there is no leakage of water into the heat source fluid or the heated fluid. Therefore, the system lends ' itself to applications in the fields of food, medical compounds, etc.
  • Embodiments of the present invention are described with reference to the accompanying drawing wherein:
    • Figure 1 illustrates schematically the arrangement of the elements comprising the heat pump.
  • Figure 1 shows the heat pump, operated at a low or medium temperature; e.g., 10 to 95°C, in which both evaporation and condensation of water is performed under a pressure less than atmospheric pressure: e.g. 1.24 x 103 to 84.8 x 103 Pa (0.18 to 12.3 psi). Heat source fluid, e.q., methanol vapor, enters from inlet 11 and condensed methanol exits from outlet 12, heating water flows in the evaporator 1. Fluid to be heated, e.g., ethanol, enters from inlet 13, is heated with steam which is condensed in the condenser 9, and exits via conduit 14. Water flowing in the heat pump evaporates while cooling or condensing. the heat source fluid in the evaporator and flows into compressor 6 after mist is removed by demister 4. Steam pressurized by compressor 6, temperature of which is raised, passes through pipe 15 and enters condenser 9.
  • Steam itself turns to condensed water by giving heat to the heated fluid in the condenser. This water flows into the evaporator 1 through pipe 16. At the end of pipe 16 in the condenser 9, the attached float valve keeps the water level in the condenser constant. The pressure reducing valve 10 is attached to the pipe 16 between the evaporator 1 and condenser 9 to maintain the required pressure difference. Since the whole system is operated below atmospheric pressure, air which enters into the system is exhausted from the top of condenser 9 through pipe 17 by vacuum generating device 8 and is discharged into the atmosphere.
  • The vacuum regulation valve 7, provided half way long pipe 17, keeps condensing pressure to the required value; e.g. 1.59 x 103 to 97.9 x 10 Pa, (0.23 to 14.2 psi). Steam is discharged from the system along with uncondensed gas, so supplementation of water becomes necessary. This supplementation of water is effected by feedwater device 3 through pipe 18.
  • The float valve 21, attached at the end of pipe 18 located in the evaporator 1, enables the water level in the evaporator to be the required level. Pipe 19 is a steam line for sealing of a seal portion of the compressor (labyrinth type). This steam flows into condenser 9 through pipe 18 along with compressed steam and further flows into evaporator 1 through pipe 16 in the form of condensed water. In the case where the quantity of steam entering into the system exceeds the quantity which is discharged by vacuum generating equipment 8, the level of water in the evaporator goes up. In this case, extra water is drained through pipe 20 by draining device 2.
  • In the case of manual-double valve type operation, excessive water is guided to a receiving pot 2 in the draining device through a float valve 22, which is connected to pipe 20 in the evaporator, holding the upper valve 23 of the draining device open. The upper valve is closed when the receiving pot is filled with water and then water is discharged by opening the lower valve 24. The load regulation of the heat pump is performed by bypass valve 5.

Claims (9)

1. A heat pump comprising an evaporator (1), a compressor (6) and a condenser (9) through which flows a refrigerant, characterized in that said refrigerant is water, said evaporator (1) is equipped with a feedwater control device (3) and a draining device (2), and said condense (9) is equipped with a vacuum generating means (8).
2. The heat pump according to claim 1, wherein said vacuum generating means exhausts uncondensed air which leaks into the heat pump via the condenser.
3. The heat pump according to claims 1 or 2, wherein the feedwater device supplies water to compensate for a decrease in the amount of water within the heat pump.
4. The heat pump according to claim 3, wherein the feedwater device includes a float valve (21) which is actuated when the water level in the evaporator falls below a set level.
5. The heat pump according to anyone of claims 1 to 3, wherein draining device drains excessive water from the heat pump.
6. The heat pump according to claim 5, wherein the draining device includes a float valve (21) which is actuated when the water in the evaporator exceeds a predetermined level.
7. The heat pump according to claim 1; wherein said evaporator includes an inlet means and an outlet means for directing a heat source fluid into and out of a heat exchanger unit located within said evaporator.
8. The heat pump according to claim 1, wherein said condenser includes inlet means and outlet means for directing a fluid to be heated into and out of a heat exchanger unit located within said condenser.
9. The heat pump according to claim 1, wherein said compressor compresses heated vapor taken from the evaporator and directs the pressurized vapor into the condenser.
EP85100154A 1984-01-10 1985-01-09 Heat pump Expired - Lifetime EP0150014B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP59002273A JPS60147067A (en) 1984-01-10 1984-01-10 Heat pump
JP2273/84 1984-01-10
JP2773/84 1984-01-10

Publications (3)

Publication Number Publication Date
EP0150014A2 true EP0150014A2 (en) 1985-07-31
EP0150014A3 EP0150014A3 (en) 1986-10-08
EP0150014B1 EP0150014B1 (en) 1990-05-02

Family

ID=11524757

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85100154A Expired - Lifetime EP0150014B1 (en) 1984-01-10 1985-01-09 Heat pump

Country Status (4)

Country Link
US (1) US4638642A (en)
EP (1) EP0150014B1 (en)
JP (1) JPS60147067A (en)
DE (1) DE3577474D1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5174126A (en) * 1990-11-09 1992-12-29 Charles Cameron Air conditioning system
WO2000006955A3 (en) * 1998-07-31 2000-09-08 Texas A & M Univ Sys Vapor-compression evaporative air conditioning system
FR2800159A1 (en) * 1999-10-25 2001-04-27 Electricite De France HEAT PUMPING SYSTEM, ESPECIALLY WITH REFRIGERATION FUNCTION

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JP2844296B2 (en) * 1993-06-29 1999-01-06 正樹 佐久間 Vacuum concentrator
FR2730556B1 (en) * 1995-02-14 1997-04-04 Schegerin Robert ERGONOMIC AND ECOLOGICAL COOLING SYSTEM
EP0833116A4 (en) * 1996-04-15 2001-09-12 Mitsubishi Electric Corp Water evaporation type cooling apparatus by means of electrolytic reaction
KR100831512B1 (en) * 2000-05-26 2008-05-22 테크놀로지스크 인스티튜트 Condenser with integrated deaerator
US7000691B1 (en) * 2002-07-11 2006-02-21 Raytheon Company Method and apparatus for cooling with coolant at a subambient pressure
US20050274139A1 (en) * 2004-06-14 2005-12-15 Wyatt William G Sub-ambient refrigerating cycle
US7866179B2 (en) * 2005-02-23 2011-01-11 I.D.E. Technologies Ltd. Compact heat pump using water as refrigerant
US7748219B2 (en) * 2005-03-23 2010-07-06 Pdm Solar, Inc. method and apparatus to convert low temperature thermal energy to electricity
JP5151014B2 (en) * 2005-06-30 2013-02-27 株式会社日立製作所 HEAT PUMP DEVICE AND HEAT PUMP OPERATION METHOD
US20070119568A1 (en) * 2005-11-30 2007-05-31 Raytheon Company System and method of enhanced boiling heat transfer using pin fins
US20070119199A1 (en) * 2005-11-30 2007-05-31 Raytheon Company System and method for electronic chassis and rack mounted electronics with an integrated subambient cooling system
US20070119572A1 (en) * 2005-11-30 2007-05-31 Raytheon Company System and Method for Boiling Heat Transfer Using Self-Induced Coolant Transport and Impingements
JP4923618B2 (en) * 2006-02-27 2012-04-25 株式会社日立製作所 Heat pump system, lubricating water temperature adjustment method of heat pump system, operation method of heat pump system
JP4779741B2 (en) * 2006-03-22 2011-09-28 株式会社日立製作所 Heat pump system, shaft sealing method of heat pump system, modification method of heat pump system
EP2341300B1 (en) 2006-04-04 2017-09-06 Efficient Energy GmbH Heat pump
US7908874B2 (en) * 2006-05-02 2011-03-22 Raytheon Company Method and apparatus for cooling electronics with a coolant at a subambient pressure
JP4992346B2 (en) * 2006-08-31 2012-08-08 株式会社日立製作所 Heat pump system, shaft sealing method of heat pump system
DE102006056798B4 (en) * 2006-12-01 2008-10-23 Efficient Energy Gmbh Heat pump with a cooling mode
DE102007005930A1 (en) * 2007-02-06 2008-08-07 Efficient Energy Gmbh Heatpipe, small power plant and method for pumping heat
US8651172B2 (en) * 2007-03-22 2014-02-18 Raytheon Company System and method for separating components of a fluid coolant for cooling a structure
US7921655B2 (en) * 2007-09-21 2011-04-12 Raytheon Company Topping cycle for a sub-ambient cooling system
US7934386B2 (en) * 2008-02-25 2011-05-03 Raytheon Company System and method for cooling a heat generating structure
US7907409B2 (en) * 2008-03-25 2011-03-15 Raytheon Company Systems and methods for cooling a computing component in a computing rack
EP2307824B1 (en) * 2008-06-23 2016-04-06 Efficient Energy GmbH Device and method for efficient condensation
JP5306751B2 (en) * 2008-09-12 2013-10-02 株式会社テイエルブイ Vapor compression refrigerator
JP5306750B2 (en) * 2008-09-12 2013-10-02 株式会社テイエルブイ Vapor compression refrigerator
JP5793670B2 (en) * 2011-04-28 2015-10-14 パナソニックＩｐマネジメント株式会社 Air conditioner
JP2012007882A (en) * 2011-08-01 2012-01-12 Efficient Energy Gmbh Heat pump
JP5490841B2 (en) * 2012-03-26 2014-05-14 株式会社ササクラ Water refrigerant heater and water refrigerant water heater using the same
CN106439766A (en) * 2016-09-30 2017-02-22 中能服能源科技股份有限公司 Steam production device and direct compression type heat pump system
CN106482087B (en) * 2016-11-28 2018-11-13 克雷登热能设备(浙江)有限公司 Steam generator water capacity measurement method and device

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CH305668A (en) * 1950-12-12 1955-03-15 Sueddeutsche Zucker Ag Method for operating a heat pump.
CH342583A (en) * 1956-06-21 1959-11-30 Rawyler Ernst Steam generation system based on the principle of the heat pump
FR2478264A1 (en) * 1980-03-13 1981-09-18 Saint Laumer Daniel De Steam generating plant with heat pump - has evaporator with heat pump circuit containing liquid condensed to heat water
FR2516205A3 (en) * 1981-11-06 1983-05-13 Saint Laumer Daniel De Economical heat pump for low pressure steam generation - has automatic controller switching heat pump motor for temp. regulation, and compressor-condenser circuit
DE3302064A1 (en) * 1982-01-26 1983-08-04 Israel Desalination Engineering (Zarchin Process) Ltd., Tel-Aviv Steam compression heat pump
EP0095439A2 (en) * 1982-05-21 1983-11-30 Siemens Aktiengesellschaft Heat pump

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Publication number Priority date Publication date Assignee Title
CH305668A (en) * 1950-12-12 1955-03-15 Sueddeutsche Zucker Ag Method for operating a heat pump.
CH342583A (en) * 1956-06-21 1959-11-30 Rawyler Ernst Steam generation system based on the principle of the heat pump
FR2478264A1 (en) * 1980-03-13 1981-09-18 Saint Laumer Daniel De Steam generating plant with heat pump - has evaporator with heat pump circuit containing liquid condensed to heat water
FR2516205A3 (en) * 1981-11-06 1983-05-13 Saint Laumer Daniel De Economical heat pump for low pressure steam generation - has automatic controller switching heat pump motor for temp. regulation, and compressor-condenser circuit
DE3302064A1 (en) * 1982-01-26 1983-08-04 Israel Desalination Engineering (Zarchin Process) Ltd., Tel-Aviv Steam compression heat pump
EP0095439A2 (en) * 1982-05-21 1983-11-30 Siemens Aktiengesellschaft Heat pump

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5174126A (en) * 1990-11-09 1992-12-29 Charles Cameron Air conditioning system
WO2000006955A3 (en) * 1998-07-31 2000-09-08 Texas A & M Univ Sys Vapor-compression evaporative air conditioning system
US6427453B1 (en) 1998-07-31 2002-08-06 The Texas A&M University System Vapor-compression evaporative air conditioning systems and components
FR2800159A1 (en) * 1999-10-25 2001-04-27 Electricite De France HEAT PUMPING SYSTEM, ESPECIALLY WITH REFRIGERATION FUNCTION
EP1096209A1 (en) * 1999-10-25 2001-05-02 Electricite De France Heat pumping device, in particular for refrigeration

Also Published As

Publication number Publication date
JPS60147067A (en) 1985-08-02
EP0150014A3 (en) 1986-10-08
JPH056105B2 (en) 1993-01-25
DE3577474D1 (en) 1990-06-07
EP0150014B1 (en) 1990-05-02
US4638642A (en) 1987-01-27

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